WO2013131214A1

WO2013131214A1 - Mixed variable flow volute

Info

Publication number: WO2013131214A1
Application number: PCT/CN2012/000557
Authority: WO
Inventors: 王航; 李永泰; 朱智富; 袁道军; 王艳霞; 宋丽华; 张金明
Original assignee: Wang Hang; Li Yongtai; Zhu Zhifu; Yuan Daojun; Wang Yanxia; Song Lihua; Zhang Jinming
Priority date: 2012-03-08
Filing date: 2012-04-25
Publication date: 2013-09-12
Also published as: CN102536435B; CN102536435A

Abstract

Disclosed is a mixed variable flow volute, comprising a turbine volute (1) within which are provided a volute intake flow path and a volute nozzle ring (13). One end of the volute intake flow path is provided with a volute air-inlet (2), and the other end thereof is provided with a volute air-outlet (3); the volute intake flow path is divided into three flow paths via partitions, i.e. a first intake flow path (4), a second intake flow path (5) and a third intake flow path (6), each of which is in communication with the volute air-inlet (2); the first intake flow path (4) is a normally open intake flow path; and intake control valves (7) are provided in the second intake flow path (5) and the third intake flow path (6) close to the volute air-inlet (2), the intake control valves (7) being able to be opened or closed depending on the operating speed of the engine so as to open or close at least one of the second intake flow path (5) and the third intake flow path (6). The mixed variable flow volute has a simple structure, low cost, high reliability and is easy to control.

Description

Hybrid variable flow volute

Technical field:

The invention relates to a variable flow volute, in particular to an air intake adjusting device, which realizes different working and working of different flow paths to meet the performance requirements of various working conditions of the engine, and can improve the performance of the medium speed condition of the engine. The hybrid variable flow volute belongs to the field of internal combustion engines.

Background technique:

With the increasingly stringent requirements of emission regulations, there is an increasing demand for superchargers that can balance the performance of the engine. The variable-section turbocharger (VGT) can effectively control the exhaust pressure of the engine. The perfect performance matching between the supercharger and the engine under various working conditions has become the focus of research and development. A variety of variable-section turbocharger configurations have been designed and developed, including variable nozzle ring boosters (VNTs), variable throat boosters, and tongue-shaped baffle boosters. However, the problem in practical application is that the engine's intake and exhaust negative pressure difference is very high, and the pumping loss is too high, resulting in high fuel consumption of the engine at low speed. At present, the dual-channel turbocharger (DLP) structure has been greatly developed. Patent CN101694166A discloses a two-layer flow path variable-section turbine control device, which comprises a turbine casing, and two inner and outer intake flows are provided in the turbine casing. In the high operating condition of the engine, the device adjusts the opening degree of the valve through the valve control mechanism to adjust the intake air amount entering the outer flow passage of the volute intake air, and realizes the function of variable cross section. However, in the high-speed working condition of the engine, the airflow mixed flow is likely to occur in the intake passage of the outer flow passage of the volute, and the airflow in the outer portion of the flow passage of the volute may have a phenomenon of returning to the outer flow passage of the volute. The performance of the engine under high working conditions.

Therefore, it is desirable to design a hybrid variable flow volute (MVP) structure with simple structure and high reliability to improve the performance of the engine under medium speed conditions, and to improve the intake air volume and efficiency of the engine at low speed conditions. Improve the boost ratio of the engine under high working conditions to meet the performance requirements of the engine under various working conditions. Summary of the invention:

The problem to be solved by the present invention is to provide a hybrid variable flow volute that satisfies the above-mentioned deficiencies of the variable-section turbocharger structure, and satisfies the performance requirements of the engine under full working conditions, particularly the performance of the medium-speed operating range of the engine.

In order to solve the above problems, the present invention adopts the following technical solutions:

A hybrid variable flow volute comprising a turbine volute, a volute inlet flow passage and a volute nozzle ring in the turbine volute; a volute inlet at one end of the volute intake passage, and One end is provided with a volute air outlet;

The volute inlet flow passages are partitioned into three flow passages through the partition plate: a first intake flow passage, a second intake flow passage, and a third intake flow passage, a first intake passage, a second intake passage, and a third intake passage Connected to the volute inlet respectively;

The first intake flow passage is a normally open intake flow passage;

The second intake flow passage and the third intake flow passage are provided with an intake adjustment valve at a position close to the volute intake port, and the intake adjustment valve can divert the airflow flowing into the first intake passage while opening or closing ;

When the engine is in the low speed range, the intake adjustment valve is closed, the second intake passage and the third intake passage are closed, and the first intake passage is in a separate working state;

When the engine is in the medium speed condition range, the intake regulating valve opens at a certain angle, the second intake flow passage is opened, and the third intake flow passage is in a closed state, at which time the first intake flow passage and the second intake flow passage are simultaneously Working status

When the engine is in the high speed working condition range, the intake regulating valve is completely smashed, and the second intake flow path and the third intake flow path are opened, and at this time, the first intake flow path, the second intake flow path and the third intake flow path At the same time working. The following is a further improvement of the above solution by the present invention:

The first intake flow path, the second intake flow path, and the third intake flow path are arranged up and down.

Another improvement: the second intake flow passage and the first intake flow passage are arranged up and down; the third intake flow passage and the second intake flow passage are arranged side by side.

Further improvement: the first intake flow passage realizes a full-circumference intake of 0-360 degrees in the circumferential direction; and the intake angle of the second intake passage in the circumferential direction is an arbitrary intake angle between 0-180 degrees, The corresponding third intake air passage has an intake angle in the circumferential direction of an arbitrary intake angle of between 180 and 360 degrees, and a sum of intake angles of the second intake passage and the third intake passage is 360 degrees.

Further improvement: The end of the intake regulating valve near the inlet of the volute is provided with an intake adjusting valve shaft integrally connected with the intake adjusting valve, and the intake adjusting valve shaft is rotatably connected with the turbine volute.

Further improvement: The cross-sectional shape of the intake adjusting valve is a fan-shaped structure, and the inner wall of the volute casing is provided in the snail inlet flow passage, and the inner wall of the turbine volute is provided with a sinking groove for accommodating the intake adjusting valve at a position corresponding to the intake adjusting valve .

Further improvement: the second intake air passage has an inner wall of the second intake flow passage, and the inner wall of the second intake flow passage is provided with an engagement surface of the intake adjustment valve matched with the intake adjustment wide door.

Further improvement: there is a gap between the partition between the second intake runner and the third intake runner and the end of the intake regulating valve, the gap is controlled between 0-5 mm to ensure reliability and reduce leakage loss .

Further improvement: a plurality of guide vanes having different installation angles are respectively disposed in the intake regions of the second intake passage and the third intake passage adjacent to the scroll nozzle ring.

The invention adopts the above solution, when the engine is in the low speed working condition range, the air intake adjusting control mechanism drives the air intake adjusting valve shaft to rotate, thereby driving the integrally connected air intake adjusting valve to rotate, at this time, the second intake air flow path and the third input The airflow passage is closed in an inoperative state, and the exhaust gas discharged from the engine only flows through the first intake airflow passage to drive the turbine impeller to work, since the flow passage area of the first intake airflow passage is small and is 360. The full-cycle intake can effectively increase the intake pressure of the turbine, increase the available energy in the exhaust gas, reduce the turbo lag, and increase the pressure ratio under low-speed conditions.

When the engine is in the medium speed condition, the intake adjustment control mechanism drives the intake adjustment valve shaft to rotate, thereby driving the intake adjustment valve to rotate. At this time, the second intake passage is opened to be in the working state, and the third intake passage is When the shutdown is in an inoperative state, exhaust gas discharged from the engine flows through the first intake flow passage and the second intake flow passage to drive the turbine impeller to work, since the cross-sectional area of the volute intake passage increases and is in the intake state, and The intake area of the intake air passage is not full-circumference intake, which can effectively meet the intake pressure of the turbine impeller at medium engine speed, improve the utilization rate of the engine exhaust gas energy, and meet the supercharge demand of the engine at medium speed.

When the engine is in the high-speed working state, the intake adjusting control mechanism drives the intake adjusting valve shaft to rotate, thereby driving the integrally connected intake adjusting valve to rotate, and at this time, the second intake runner and the third intake runner are opened to work. In the state, the exhaust gas discharged from the engine flows through the first intake flow path, the second intake flow path, and the third intake flow path to drive the turbine impeller to work, because the cross-sectional area of the volute intake flow passage is the largest and the intake state, and An intake passage is 360 degrees full-cycle intake, and a sum of angles of intake regions of the second intake passage and the third intake passage is 360 degrees, and exhaust gas discharged from the engine flows through the first intake passage and the second intake respectively The airflow path and the third intake flow path enter the turbine wheel in a full-cycle intake. With the joint work of all the runners, a reasonable distribution of the turbine intake flow is achieved, thereby increasing the boost ratio.

The invention has good inheritance, low cost and easy and quick realization of engineering. The air intake adjusting device in the structure has a simple structure, the control method is easy to implement, and the reliability is high.

The invention will be further described below in conjunction with the drawings and embodiments.

BRIEF DESCRIPTION OF THE DRAWINGS:

1 is a schematic structural view of Embodiment 1 of the present invention;

Figure 2 is a cross-sectional view taken along line AA of Figure 1; Figure 3 is a schematic structural view of a volute air inlet of Embodiment 1 of the present invention;

Figure 4 is a perspective view showing the structure of an intake adjusting valve in Embodiment 1 of the present invention;

Figure 5 is a plan view showing the structure of an intake adjusting valve in Embodiment 1 of the present invention;

Figure 6 is a schematic structural view of Embodiment 2 of the present invention;

Figure 7 is a cross-sectional view taken along line B-B of Figure 6;

Figure 8 is a schematic structural view of a volute air inlet of Embodiment 2 of the present invention;

Figure 9 is a perspective view showing the structure of an intake adjusting valve in Embodiment 2 of the present invention;

Figure 10 is a plan view showing the structure of an intake adjusting valve in Embodiment 2 of the present invention;

Figure 11 is a schematic view showing the structure of a volute air inlet in Embodiment 3 of the present invention.

In the figure: 1-turbine volute; 2- volute inlet; 3- volute outlet; 4-first intake runner; 5- second intake runner; 6-third intake runner; 7- Intake regulating valve; 8-intake regulating valve shaft; 9 - turbine volute inner wall; 10- second intake runner inner wall; 11-intake regulating valve mating surface; 12-sinking groove; 13- volute nozzle ring; 14-guide vanes.

detailed description:

Embodiment 1, as shown in FIG. 1, FIG. 2, FIG. 3, a hybrid variable flow volute including a turbine volute 1 in which a volute intake flow passage and a volute nozzle ring 13 are disposed One end of the volute inlet flow passage is provided with a volute air inlet 2, and the other end is provided with a volute air outlet 3.

The volute inlet flow passage is divided into three flow passages arranged up and down through the partition plate: a first intake flow passage 4, a second intake passage 5 and a third intake passage 6, a first intake passage 4, and a second inlet The air flow path 5 and the third intake air flow path 6 are in communication with the volute air inlet 2, respectively.

The first intake runner 4 is a constant intake passage; the first intake runner 4 achieves a full circumference intake of 0-360 degrees in the circumferential direction. The angle of the intake region of the second intake passage 5 in the circumferential direction is an arbitrary intake angle between 0 and 180 degrees, and the angle P of the corresponding intake region of the third intake passage 6 in the circumferential direction is 180- The arbitrary intake angle between 360 degrees, the sum of the intake angles of the second intake runner 5 and the third intake runner 6 is 360 degrees.

The second intake passage 5 and the third intake passage 6 are provided with an intake adjustment valve 7 at a position close to the volute intake port 2, and the intake adjustment flap 7 can be supplied to the first intake flow while being opened or closed. The airflow of the track 4 is diverted.

An end of the intake adjusting valve 7 near the volute inlet 2 is provided with an intake adjusting valve shaft 8 connected to the intake adjusting valve 7 , and the intake adjusting valve shaft 8 is rotatably connected with the turbine volute 1 . The adjustment valve shaft 8 is rotated by the intake adjustment control mechanism to drive the integrally connected intake adjustment valve 7 to rotate, so that the second intake flow passage 5 and the third intake passage 6 are in an open or closed state.

When the engine is in the low speed range, the intake regulator valve 7 is closed, and the second intake runner 5 and the third intake runner 6 are closed, at which time the first intake runner 4 is in a separate operating state.

When the engine is in the medium speed range, the intake regulating valve 7 opens at a certain angle, the second intake runner 5 is opened, and the third intake runner 6 is in a closed state, at which time the first intake runner 4 and the second intake The airflow path 5 is in operation at the same time.

When the engine is in the high speed working condition range, the intake regulating valve 7 is fully opened, and the second intake flow passage 5 and the third intake flow passage 6 are opened, at this time, the first intake runner 4, the second intake runner 5, and the first The three intake air passages 6 are simultaneously in operation.

As shown in Figs. 4 and 5, the cross-sectional shape of the intake regulating valve 7 is a sector structure.

As shown in FIG. 2, the volute inlet flow passage has a turbine volute inner wall 9, and the inner wall 9 of the turbine volute is provided with a sinking groove 12 for accommodating an intake regulating valve at a position corresponding to the intake regulating valve 7. .

The second intake passage 5 has a second intake passage inner wall 10, and the second intake passage inner wall 10 is provided with an intake adjustment valve fitting surface 11 that cooperates with the intake adjustment valve 7. There is a gap h between the partition between the second intake runner 5 and the third intake runner 6 and the end of the intake regulating wide door 7, which gap is controlled between 0-5 mm. To ensure reliability and reduce leakage losses.

a plurality of guide vanes (not shown) having different mounting angles are respectively disposed in the air intake regions of the second intake air passage 5 and the third intake air passage 6 adjacent to the scroll nozzle ring 13 to The intake air flow induced into the second intake flow passage 5 and the third intake flow passage 6 enters the turbine at a suitable air flow angle.

Embodiment 2, as shown in FIG. 6, FIG. 7, and FIG. 8, this embodiment is another modification performed on the basis of Embodiment 1, a hybrid variable flow volute including a turbine volute 1, A volute inlet flow passage is provided in the turbine volute 1.

One end of the volute inlet flow passage is provided with a volute air inlet 2, and the other end is provided with a volute air outlet 3. The volute inlet flow passage includes three working flow passages: a first intake runner 4, a second intake runner 5, and a third intake runner 6, a first intake runner 4, a second intake runner 5, and a third inlet The air flow paths 6 are in communication with the volute air inlet 2, respectively.

The second intake passage 5 and the first intake passage 4 are arranged one above the other; the third intake passage 6 and the second intake passage 5 are arranged side by side.

A plurality of guide vanes 14 having unequal mounting angles are respectively disposed in the second intake air passage 5 and the third intake passage 6 in the intake region adjacent to the volute nozzle ring 13. The helium gas stream induced to enter the second intake flow path 5 and the third intake flow path 6 enters the turbine at a suitable gas flow angle.

As shown in FIG. 7, FIG. 9 and FIG. 10, the arrangement of the intake regulating valve 7 of the present embodiment is the same as that of the intake adjusting valve 7 of the first embodiment, and is used for control by the intake adjusting control mechanism. The opening or closing of the intake regulating valve 7 achieves opening or closing of the second intake runner 5 and the third intake runner 6.

The present invention adopts the above two design schemes, and the working process is the same.

As shown in Fig. 2 and Fig. 7, when the engine is in the low speed range, the intake adjustment control mechanism drives the intake adjustment valve shaft 8 to rotate, thereby driving the integrally connected intake adjustment valve 7 to rotate, and the intake adjustment The position of the valve 7 is shown by the solid line in FIG. 2 and FIG. 7. At this time, the second intake flow passage 5 and the third intake flow passage 6 are closed in an inoperative state, and the exhaust gas discharged from the engine flows only through the first intake passage. 4, the turbine impeller is driven to work, because the first intake passage 4 has a small flow cross-sectional area and 360 degrees of full-circumference intake, which can effectively increase the intake pressure of the turbine, increase the available energy in the exhaust gas, reduce turbo lag, and improve Pressure ratio at low speed conditions.

When the engine is in the medium speed condition, the intake adjustment control mechanism drives the intake adjustment valve shaft 8 to rotate, thereby driving the integral connection of the intake adjustment valve 7 to rotate, and the position of the intake adjustment valve 7 is as shown in FIG. 2 and FIG. As shown by the line, at this time, the second intake passage 5 is opened to be in an operating state, the third intake passage 6 is closed in an inoperative state, and the exhaust gas discharged from the engine flows through the first intake passage 4 and the second intake passage. 5 thus driving the turbine impeller to work, because the cross-sectional area of the volute inlet flow passage is large and the intake state, and because the intake region of the second intake runner 5 is not the full-cycle intake, it can effectively meet the engine entering the turbine at medium speed. The intake pressure of the impeller increases the utilization of the exhaust energy of the engine and meets the boost requirement of the engine at medium speed.

When the engine is in the high-speed working state, the intake adjusting control mechanism drives the intake adjusting valve shaft 8 to rotate, thereby driving the integral connection of the intake adjusting valve 7 to rotate, and the position of the intake adjusting wide door 7 is as shown by the dotted line in FIG. 2 and FIG. At this time, the second intake flow passage 5 and the third intake flow passage 6 are opened to be in an operating state, and the exhaust gas discharged from the engine flows through the first intake passage 4, the second intake passage 5, and the third intake passage 6 so that The turbine impeller is driven to work, because the cross-sectional area of the volute inlet flow passage is the largest and the intake state, and since the first intake passage 4 is 360-degree full-cycle intake, the second intake runner 5 and the third intake runner 6 The sum of the angles of the intake regions is 360 degrees, and the exhaust gas discharged from the engine flows through the first intake runner 4, the second intake runner 5, and the third intake runner 6, respectively, and enters the turbine impeller in a full-cycle intake manner. Under the common work of all the runners, a reasonable distribution of the turbine inlet flow is achieved, thereby increasing the boost ratio.

Embodiment 3, the above Embodiment 1 and Embodiment 2 are adapted to a constant pressure supercharged engine, as shown in FIG. By combining the two identical structures (two sets of flow paths) designed in Embodiment 1 and Embodiment 2 by a certain combination of structures (each group of flow paths corresponding to one engine exhaust manifold flow path) is adapted to pulse increase Press the engine, the volute air inlet is designed to be two.

The design of the volute inlet flow passage is not limited to the three embodiments described above, and will be divided into three flow passages of a first intake flow passage, a second intake flow passage and a third intake flow passage, and may also be according to special needs. The two intake runners are divided into a plurality of intake runner branches, and the third intake runners are divided into a plurality of intake runner branches. According to the arrangement of the two flow path structures in the first embodiment and the second embodiment, the first intake air flow path is still set to 360 degrees of full-circumference intake and the normally-opening intake flow path, and the second intake air flow path is set. The air intake passages of the air passages are all non-full-cycle intake, and the sum of the angles of the plurality of intake regions of the second intake runner is 0 to 180 degrees of non-peripheral intake; setting a plurality of intake flows of the third intake runner The intake area of the track is non-full-cycle intake, and the angle values of several intake regions of the third intake runner are 180 to 360 degrees of non-full-cycle intake. An intake adjusting valve conforming to the cross-sectional shape of the above-mentioned scheme is disposed at an intake port of the second intake air passage, and the intake adjusting valve is opened and closed according to various working conditions of the engine, thereby realizing the second intake flow path if the branch and the first The working or inoperative state of several branches of the three intake runners. The structural improvement works in the same manner as in the above embodiment.

Claims

Rights request

A hybrid variable flow volute comprising a turbine volute (1), wherein the turbine volute (1) is provided with a volute inlet flow passage and a volute nozzle ring (13); One end of the airflow passage is provided with a volute air inlet (2), and the other end is provided with a volute air outlet (3);

The volute inlet flow passages are partitioned into three flow passages through the partition plate: a first intake flow passage (4), a second intake passage (5), and a third intake passage (6), the first intake flow The passage (4), the second intake passage (5) and the third intake passage (6) are respectively connected to the volute inlet (2);

The first intake runner (4) is a normally open intake runner;

The second intake flow passage (5) and the third intake flow passage (6) are provided with an intake adjustment valve (7) at a position close to the volute intake port (2), and the intake adjustment valve (7) The airflow flowing into the first intake air passage (4) can be diverted while being opened or closed;

When the engine is in the low speed range, the intake adjustment valve (7) is closed, and the second intake passage (5) and the third intake passage (6) are closed, and the first intake passage (4) Being in a single working state;

When the engine is in the medium speed condition range, the intake adjusting valve (7) opens at a certain angle, the second intake flow passage (5) is opened, and the third intake flow passage (6) is closed, and the first is The inlet air passage (4) and the second intake passage (5) are simultaneously in operation;

When the engine is in the high speed range, the intake regulating valve (7) is fully opened, and the second intake runner (5) and the third intake runner (6) are opened, and the first intake runner (4) ), the second intake runner (5) and the third intake runner (6) are simultaneously in operation.

2. A hybrid variable flow volute according to claim 1, wherein: said first intake runner (4), second intake runner (5) and third intake runner (6) ) Arrange up and down.

3. The hybrid variable flow volute according to claim 1, wherein: the second intake flow passage (5) is arranged above and below the first intake flow passage (4); the third intake flow The road (6) and the second intake runner (5) are arranged side by side.

A hybrid variable flow volute according to claim 2 or 3, wherein: said first intake passage (4) achieves a full circumference intake of 0-360 degrees in the circumferential direction; The second intake passage (5) has an intake angle angle (α) in the circumferential direction of any intake angle between 0 and 180 degrees, and the corresponding third intake passage (6) advances in the circumferential direction. The gas zone angle is any intake angle between 180-360 degrees, and the sum of the intake angles of the second intake runner (5) and the third intake runner (6) is 360 degrees.

5. A hybrid variable flow volute according to claim 4, wherein: said one end of said intake air regulating wide door (7) adjacent to said volute inlet (2) is provided with intake air The regulating valve (7) is a body-connected intake adjusting valve shaft (8), and the intake adjusting valve shaft (8) is rotatably coupled to the turbine volute (1).

6. The hybrid variable flow volute according to claim 5, wherein: the cross-sectional shape of the intake adjusting valve (7) is a fan-shaped structure, and the volute casing has a turbine volute The inner wall (9), the inner wall (9) of the turbine volute is provided with a sinking groove (12) for accommodating the intake adjusting valve at a position corresponding to the intake regulating wide door (7).

7. The hybrid variable flow volute according to claim 6, wherein: the second intake flow passage (5) has a second intake runner inner wall (10), and the second intake runner The inner wall (10) is provided with an intake adjusting wide door fitting surface (11) matched with the intake adjusting wide door (7).

8. A hybrid variable flow volute according to claim 7, characterized by - a diaphragm and an intake regulating valve between the second intake runner (5) and the third intake runner (6) There is a gap (h) between the ends of (7), and the gap (h) is controlled between 0-5 mm.

9. A hybrid variable flow volute according to claim 8, wherein: said second intake runner (5) and said third intake runner (6) are adjacent to the volute nozzle ring A plurality of guide vanes (14) having different mounting angles are respectively arranged in the intake region of (13).